Rotary pump and packing therefor



I Dec. 2s, 1.948.

ROTARY PUMP AND PACKING THEREFOR Original Filed June 12, 1941 2 Sheets-Sheet 1 M/CHEL 5 CflSERT/l M. CASERTA 2,457,643

Patented Dec. 28, 1948 UNITED STATES PATENT OFFICE Original application June 12, 1941, Serial N0. 397,763. Divided and this application March .24, 1943, Serial No.480,278

6 Claims.

This invention relates to a rotary pump and more particularly, although not so restricted, to the type used in aircraft fuel transfer installations.

The subject matter of this application has been divided from my :copending patent application Serial 397,763, filed June .12, 1941, entitled Fluid transfer mechanism now Patent No. 2,353,545, issued July 11, 1944.

Usually in such installations a pump, driven for instance by the engine, transfers the gasoline or other fuel from the reservoir to the carburetor or other distributing device.

An object of the present inventiton is to provide a rotary pump which i simple, compact, light, easily manufactured and assembled, and generally eflicient.

A further object of the invention is to provide a rotary pump, having a chamber which is closed atone end and open at the other to receive therethrough the elements of the pump for assembly in said chamber, and having a sealing gland for said open :end that extends into said chamber for cooperation with said pump elements and that provided with an integral end abutment flange for attachment to said open end to hold said pump elements in assembled relationship.

A further object of this invention is to provide a rotary pump having .a cup-shaped chamber into which the pump elements may :be simply inserted for assembly without the use of special tools and in which said elements may be held :in assembled relationship by a sealing gland that closes the open end .of said chamber and that hold said pump elements in assembled relationship These and other objects will be more apparent from the following description and from the accompanying drawings.

Figures 1, '2, and 3 are an end View, a side elevational view, and a plan view, respectively, .of a fuel pump embodying the present invention, Figure 3 showing also partly in section a fragment of a mounting flange to which said pump may be attached, and some of the mounting bolts.

Figure 4 is an elevation-a1 View of the flange end only of said pump.

Figure 5 is a cross-sectional view taken substantially on line V-V of Figure '2, some .of the parts being left in elevation for clearness of illustration.

Figure .6 is a similar cross-sectional view taken substantially .on line VIVI of Figure 5.

On the drawings:

.Iihe fuel pump assembly is indicated by the nu- (Cl. 10313B.)

1 9 and includes a pump housing 11, a valve housing JLand aeover 1.3.

The pump housing ll is provided with a bore M, terminated by an end wall or thrust face 1.5.. In said bore 14 are lodged, in line and preferably press fitted, a thrust bearing 15, a first journal bearing H, an eccentric pump chamber or liner I 8 and a second journal bearing I79. A pin prevents the rotation of parts It to I18 relative to each other and relative to housing ll, while pin 21 prevents the relative rotation of chamber I 8 and bearing 19.

A straight cylindrical rotor 22 is supported in bearings I] and L9, .and is provided atone end with a splined hole 23 through which it may be driven, and with four radial slots 24, through which the vanes 25 slide. v

A ring or pump gasket 26, preferably made of resilient or deformable material such as for instance synthetic rubber, pressed against hearing H! by the beveled end 21 of gland 2B,, which is assembled to the flange 29 .of the pump housing I] by means of screws an (Figures vZand 4). The

parts are preferably so proportioned that when the screws 30 are tightened, bearings It and I],

liner l8 and bearing I9 are all pressed against the end wall 15, and seal ring 26 is compressed and preferably deformed to produce a fluid tight seal between bore 14 and gland 2.8, and so Prevent the passage of fluid from the pump side 31 of gland 28 to the other or outer .side 32 along said bore. Excessive squeezing Of the pump seal ring 26 is prevented by the gland flange 33 which comes in contact with flange 2.9.

When the whole pump is assembled to an engine mounting flange 3.4 by means of the usual bolts 3-5 and nuts '36,, the heads of screws 30 are covered by said flange .34 and theza-dditional powerful action of nuts 35 holds together flanges .3'3 and 29. It is thus clearly ap arent that by my structure I avoid the use of large threaded bodies such as are .used in some structures in which a, large gland threaded into a housing, and not only do I avoid the danger of seizure of such large threads, particularly if the parts are made of aluminum, but I also avoid the expensive tools and operations necessary for such threads, and at assembly completely exclude the human element as a factor in the tightness and -compression of the pump seal. Furthermore, I do not need to make screws so very accurate or strong, nor do I need .to lock them, .as they are relied upon only to hold the parts together .during storage and tnansit,'while when the pump is in operatlon all the parts are securely held by the Gland 28 is provided with a land 31 (Fig. 6) which holds it in central position relative to the."

bore I4, and with a concentric land 38 which is useful in mounting the pump assembly centrally on, for instance, the mounting flange 34 usually;

provided for it on the engine (not shown).

In its central portion, the gland 28 is also provided with an inner flange 39 and recessed seat 40, with four radially spaced openings 4I- preferably cored out in casting soas toleave four pillars 42, and with a second inner flange 43. A ring or gasket 49 of soft or resilient material such for instance as synthetic rubber, is lodged in the recessed seat 49 and supports centrally and squarely with the bore a seal'seat 50, preferably made of wear resistance material such as bronze.

A shaft I'is provided with two splined ends, one, 52, for driving the rotor 22, and the other,

53, for 'connection to the pump driving means. The shaft5, is also provided with a flange 54 which is pressed against said seal seat by means of a spring 55, and with a second flange 56 substantially in line with the flange 43 with which it forms a wall of protection for the inside of the pump against the introduction of foreign matter. It is clear that the rubber gasket 49 is helpful in taking care of misalignment between the shaft 5! and the gland 28 or mounting flange 24, and by its resiliency allows the seal seat 50 to follow flange 54 in its possibly wabby movement, and so efiectively prevents leaks past said seat.

' The spring 55 at the other end presses against said rotor 22, which in turn rests against the thrust bearing I6.

The pump housing II is provided with two cavities or openings and BI symmetrically opposite each other with reference to the rotor 22 and with two ports 62 and 63 connected thereto, respectively. The pump will operate in either direction but for the purpose of simplicity of description'we will assume that it is operating in anti-clockwise direction, as shown by an arrow 64 in Figure 5. Then, cavity 60 and port 62 will be on the inlet or low pressure side, and cavity 6} and port 63 will be on the outlet or high pressure side. I I

The valve housing I2 and valve cover I3 are fastened to the pump housing II by means of bolts 65, which are preferably located in plan view according to a pattern symmetrical with reference to the pump axis, so that the valve housing can be inverted or rotated 180 when the pump is operated in clockwise direction.

' The valve housing I2 is provided with an outlet or pressure side opening or chamber 66 which communicates with the outlet port 63 of the pump, and which for simplicity of description 7 willalso be called the lower chamber; and with an inlet or suction side opening or chamber 61 which communicates withthe inlet port 62 and which will also be called the upper chamber, with the understanding, however, that the expressions upper and lower do not in any manner define or limit the relative location of said chambers to each other or to the pump housing.

Said chambers are separated by a partition or wall 68 which is provided with a port orvalve seat 69, which may be closed by relief valve 10.

The lower part of said relief valve 19 terminates in a cylindrical portion II which is guided in a bore 12 provided in the lower wall 13 of said valve housing I2, while the upper part i5 is also cylindrical and is guided in a bore 16.

The upper surface TI (Fig. 5) of pump housing II, the bore I2, and the valve lower wall I3 confine a space or dash-pot cavity I3. A gasket I9 is preferably provided between said pump housing i I and said valve housing I2.

The relief valve I9 itself is divided into two .sections by a horizontal wall 89 (Fig. 6) which provides an opening or seat 8I in which a bypass valve seat 82 is lodged. A by-pass disc or valve 83 is pressed against said valve seat 82 by a spring 84 and completes the horizontal wall of elements 68, 80, 82, and 83 which close communication between the upper and lower chambers.

The numerals 85 and 86 indicate ribs cast in the valve housing I2 to stiffen the structure and promote smooth-er flow ofthe fluid therethrough.

The relief valve 10 is provided with upper lateral ports 89 and lower lateral ports I06, and by-passvalve seat 82 is provided with lateral ports IBI and an axial port I02.

A diaphragm IE3 is held in fluid tight manner at its outer edge between the valve housing I2 and the cover I3, and rests in its central portion against the by-pass valve seat 32. On diaphragm I03 is mounted a washer I04 provided with a seat N35 for a ball I96, which in turn is held at its upper side in a seat I01 provided in a spring washer I08. Said washer I98 carries on'its locating seat I09 an adjusting spring IEO which at its upper end presses against a seat III of an adjusting washer II2 .into which an adjusting screw I I3 is threaded.

The valve c-over I3 is formed with a bore H4 and a counterbore or seat II5. Said adjusting screw II3is provided with a flange H6 which rests in the counterbore H5, and with an upper threaded stem III which fits into the bore I I4 and may be clamp-ed tight to the cover I3 by means of a check nut H8, or may be rotated, for instance, by means of screw driver'slot H9.

The valve cover I3 is provided on the insidev with a vertical groove I20 in which a finger I2! of the washer I I2 can slide up and down while at the same time preventing said washer H2 from rotating. When the adjusting screw H3 is turned, said'flnger I2I prevents the-washer II'2 from rotating and the consequent action of the threaded hole I22 in the center of said washer II2 compels said Washer to move up and down and so adjust the spring tension as desired.

An important advantage of this construction is that the flange II6 of the adjusting screw H3 is pressed against its seat H5 at all times by the tension of said spring III] and therefore is prevented from accidental rotation by the resultant friction and has no tendency to lose its adjustment even if the check nut I I8 is left loose. Furthermore said flange I I6 by being pressed against its seat provides a fluid tight closure, the effectiveness of which is only increased by the application of supercharger pressure above the diaphragm, for instance, througha port I23.

It will be seen that as the rotor 22 and vanes 24 rotate in the direction indicated by the arrow 64, the fluid is carried from the inlet or low pres sure port 60 to the outlet or high pressure port BI, and if the free flow thereafter is impeded,

pressure is built up on the outlet side.

-When the pressure attains a predetermined value, the relief valve is lifted from its seat 69 against the opposing action of the spring 11 0, and the fluid flows between said seat 69 and valve In and through the port -5 back to the inlet side and to said openings 62 and 80.

Should there be any tendency for the liuid pressure to pulsate, and therefore for the valve.

10 to vibrate or bounce on and on its seat, it will be seen that the lower part H of said valve will act as a piston in the cylinder 12 and trap fluid in the chamber T18, :50 that a dash-pot action will beo'btained and the vlbrationsbf said valve 10 will be minimized.

Should it be desirable to pump fluid from the port 80 to the port 61 by means independent from the pump proper, for instance when the pump is out of order or when the engine is. not turning, the fluid from the inlet ports =60 and 62 will pass through ports 61, 89, 'li0l and 1-02, will lower the valve disc :83 against the force of the spring 8.4, and after passing through the ports I00, :58, and :63 will reach the outlet port 6L .It is clear that the disc 53 may be made very light and-thin, and of light material such as bakeli'te. Furthermore, said disc 83 is normally pressed against its seat 82 by the fluid pressure on the outlet side, so that the spring 4 may be very light, with the result that the drop of pressure of fluid. lay-passed through the valve will be very small.

It a known fact that it is very difficult to produce springs whose ends will stay naturally parallel when free and when under tension. Usually, as the spring is compressed, its ends tend to twist out of parallel and form an angle, and the direction of the spring action does not remain axial. In other words it may be said that if one end is held stationary and the other one is compressed, said other one will tend to rotate as it moves axially, and the spring will give a torque component besides the expected axial reaction component.

.This is .an important factor in bringing about stickiness in valves that are spring pressed, as the'torque component will twist the valve sideways against its guiding means, causing the valve to stick and bind. The present invention provides means whereby any spring tendency to twist spends itself freely and no binding action is transmitted to the valve.

In fact, if the lower face of the spring H0 has any tendency to twist or rotate it can freely do so, as it rests on the washer I08 which can freely rotate around ball 106, which in turn transmits only :an axial component of .force to the Washer 104, which, through the diaphragm I03 and the valve seat 82 presses 0n the valve 10.

It will be noted that the adjusting screw H3 is held or guided on the vertical axis of the pump and valve assembly by the bore H4 and counterbore H5, and in turn holds and guides on said axis the adjusting washer H2, which in turn through the shoulder Hi guides the spring H0. The lower end of said spring .110 rests around the shoulder 1 0.9 and centers the washer 108, While ball I06 resting in seats I01 and 105 centers the washers I08 and I04, so that washer 104 is finally held on the .axis of the valve assembly without having any lateral guides which might introduce friction and binding action. In conclusion, there is nothing in the valve assembly constructed in accordance with the present invention that can produce binding action, and the result, confirmed in practice, is that said valve ID 'is extremelyjfree in its movement and gives very sensitive pressure control.

assume The structure described will give best results if-the spring is of ratherlarge diameter in proportion to its length, so it will rest squarely at both ends and .keep the parts in line at assembly. 7

The valve seat 5'9, the diaphragm H73, and the related parts are preferably soproportioned that the eifectivearea of the diaphragm equals the effective areanf the relief valve 10, so that variations in the fuel pressure at inlet side will have no influence on the pressure regulation. Furthermore, pressure is applied to the upper side of the diaphragm, for instance by means of the engine supercharger acting throughthe port I23, the result will be the .same as ifjsaid pres:- sure were "applied directly on the top of the relief valve, namely, the. outlet pressure adjustment will be increased indirect proportion to the,

supercharger pressure applied.

Itwill be noted that diaphragm tilt is "preferably made of resilient and easily compressible material such for instance as synthetic rubber. The shoulder, groove, or free space .124 left between the valve housing [.2 and the cover I3,

in valves provided with diaphragrns known,

in the art we usually find bolts that :go through the diaphragm and washers and nuts to fasten rods or :similarparts to the diaphragm andpick up its action. The holes in the diaphragm material and the squeezing action of the bolts and washers area continuous source of trouble, as the holes provide a good starting point i or diaphragm cracks. Furthermore, the nuts or clamping means are often assembled too loose'and produce a leakgbr too tight and squeeze and break the diaphragnnwith leaks again as a result. Other known structures resort to deep dravm or bellow shaped diaphragms which are expensive to manu facture and unreliable in service. The present invention allows the use of the simplest form of diaphragm, a plain fiat disc, without any central holes or' Tightening mean-s. Of course such a flat diaphragm is usually preferable, but other typesol diaphragms or bellows or equivalent pressure responsive means known in the art could be substituted without departing from present invention. I

The-spring 1'10 presses the washer it' l against thejdiap'hragm 1'03 and the diaphragm against the by-pass valve seat member 82 which rests on relief valve 10. Whether said relief valve 70 is resting on its seat 69 or is lifted by the outlet pressure, the spring pressurekeeps the diaphragm the spirit of the tightly held between the washer 1M and the valve seat member 82; and said diaphragm transmits its action upwards against the spring H0 or downwards against the valve seat member '82 and thereby on to the valve 10, as the case may be.

In a similar manner the by-pass valve seat member 82 is pressed in a fluid-tight manner against the relief valve "Ill by the spring 1 H3 without'the use of further fastening means.

The result of this construction is that when the four screws '55 thathold the valve assembly tor gether are released, all of the valves and related It can be noted that fuel pressures used at present in aircraft installations are mostly in the.

range of 3-20 lbs. per square inch, and as a consequence if the relief valve area is for instance one and a half square inches, spring H should be adjusted to a tension of approximately 45 to 30 pounds. On the other hand, the by-pass spring 84 is preferably made as lightas possible, and since it is assisted by the outlet pressure in keeping the valve disc 83 closed, it is usually made just strong enough to hold the disc 83 up to the valve seat member 82 against gravity and vibrations. The ratio of tension between the spring H0 and the spring 84 may thus be of the order of 400:1 to 3000:1, and the action of the spring 84 in tending to lift the valve seat member 82 from the valve 10, thereby counteracting the tension of the spring I 10, may be disregarded.

No claim is made in the present application to any particular type of bore in the pump chamber I8, nor to any particular type of vanes operable therein, many being known in the art.

It will, of course, be understood that various details of construction may be varied through a wide range without departing from the principles of this invention and it is, therefore, not the purpose to limit the patent granted hereon otherwise than necessitated by the scope of the appended claims.

What I claim is:

1. In a fluid transfer mechanism including a pump housing providing a cylindrical bore closed at one end and open at the other end, a thrust bearing in said bore adjacent said closed end, a pair of spaced journal bearings, a pump liner positioned between said journal bearings, a rotor journaled in said journal bearings for rotation within said liner and having at one end a driving connection, a shaft cooperating with said connection for driving said rotor and provided with a fixed peripheral flange, and a spring surrounding said shaft and compressively confined between said rotor and said flange, the improvement which comprises providing an attaching flange at the open end of said housing, a gland having an outer peripheral flange adapted to overlie the face of said attaching flange and to be secured thereto, said gland having an intermediate restricted portion providing an annular shoulder and having an inwardly extending annular portion slidably fitting said cylindrical bore and terminating adjacent the outer of said bearings, a resilient packing held under compression by said gland annular portion against said outer bearing and the bore wall, a seal ring between said shaft flange and said annular shoulder on said gland, and a mounting flange for said pump secured to said attaching flange with said gland flange clamped therebetween.

2. In a fluid transfer mechanism including a pump housing providing a cylindrical bore closed.

at one end and open at the other end, a thrust, bearing in said bore adjacent said closed end, apair of spaced journal bearings, a pump liner positioned between said journal bearings, a rotor journaled in said journal bearings for rotation within said liner and having at one end a driving connection, a shaft cooperating with said connection for driving said rotor and provided with a fixed peripheral flange, and a spring surrounding said shaft and compressively confined between said rotor. and said flange, theimproveequal ease and without ment which comprises providing anattaching flange at the open end of said housing, a glandv slidablyinsertable in the open end of said bore to fit snuglytherein and provided with an outer peripheral flange adapted to overlie the face of said attaching flange and be secured thereto, said gland-having an intermediate shouldered portion fa'cingiinwardly toward said shaft flange, a resiliev ent gasket seated in said shouldered portion, a seal ring mounted between said gasket and said shaftzflange, said gland also having an inwardly,

extending annular portion slidably fitting said bore and terminating adjacent the outer of said bearings, anda resilient packing compressively held'by said glandannular portion against said outer bearingand the bore wall to sealthe same.

3. In a fluid transfer mechanism including a pump housing providing a cylindrical bore closed at one end and open at the other end, a thrust bearing in said bore adjacent said closed end, a pair of spaced journal bearings, a pump liner positioned between said journal bearings, a rotor journaled in said journal bearings for rotation within'said liner 1 and having at one end a driving connection, a shaft cooperating with said 'oonnectionfordriving said rotor and provided with a fixed peripheral flange, and a spring surrounding said shaft and compressively confined betweensaid rotor and said flange, the improvement which comprises providing an attaching flange at the'open end of said housing, a gland slidably insertable' in the open end of said bore to fit snugly therein and provided with an outer peripheral flange adapted to overlie the face of said attaching flange and be secured thereto, said gland having an intermediate shoulderedportion facing inwardly toward said sha'ft flange,

a resilient gasket seated in said shouldered portion, a seal ring mounted between said gasket and said shaft flange, said gland also having an inwardly extending annular portion slidably fitting said bore and terminating adjacent the outer of said bearings, a resilient packing compressively held by said gland annular portion against said outer bearing and the bore wall to seal the same, a mounting flange for said pump overly-' ing the peripheral flange of said gland and fastening means passing through said attaching flange, gland flange and mounting flange to hold the parts of said pump together during operation.

4. In a fluid transfer mechanism including a pump housing providing a cylindrical bore closed at one end and open at the other end and pump parts operatively assembled within said bore, the improvement'for maintaining said pump parts in assembled relationship during shipment which comprises providing said pump housing with an attaching flange at said open end'of said housing, a gland slidably insertable in the open end of said bore and having an inner annular portion fitting snugly within said bore and'bearing against some of said pump parts toholdthe same in assembled relationship and provided,

with an outer peripheral flange overlying said attaching flange, and means securingsaidtwo flanges together tohold said pump parts inaslsembled relationship. e

5. In a fluid transfer mechanism including a pump housing providing. a cylindrical bore closed at one end and open at the other end and pump parts operatively assembled within said bore, the improvement for maintaining said pump parts in assembled relationship during shipment and during operation which comprises providing said pump housing with an attaching flange .at said open end of said housing, a gland slidably insertable in the open end of said bore and having an inner annular portion fitting snugly within said bore and bearing against some of said pump parts to hold the same in assembled relationship and provided with an outer peripheral flange overlying said attaching flange, means securing said tWo flanges together to hold said pump parts in assembled relationship, a mounting flange overlying said attaching flange, and pump mounting means passing through all three of said flanges to hold the same tightly together and to reinforce said flange securing means in holding said pump parts in proper assembled relationship during operation.

6. The combination with an engine mounting flange of a pump for mounting thereon, said pump comprising a housing having an end flange, pump elements including an outer thrust ring operatively assembled within said housing, a closure member having an end flange overlying said housing end flange and having an inwardly extending portion slidably insertable into said housing to confine said thrust ring in place, fastening means securing said tWo end flanges together to hold said pump elements in assembled relationship Within said housing, and other fastening means securing all three of said flanges 10 together with said closure member end flange clamped between said housing flange and said engine mounting flange.

MICHELE CASERTA.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,944,648 Saussard Jan. 23, 1934 1,989,900 Vickers Feb. 5, 1935 2,141,171 Centervall Dec. 27, 1938 15 2,189,675 Parker Feb. 6, 1940 2,192,588 Heckert Mar. 5, 1940 2,212,833 Huber Aug. 27, 1940 2,263,091 Johnson Nov. 18, 1941 2,268,804 Curtis Jan. 6, 1942 20 2,280,392 Herman, et al Apr. 21, 1942 2,289,441 Le Valley, et a1 'July 14, 1942 2,318,337 Schlosser May 4, 1943 2,351,817 Johnson June 20, 1944 25 FOREIGN PATENTS Number Country Date France Aug. 21, 1925 

